CN104385874A - Resonant frequency self-tracking giant magnetostrictive vehicle suspension vibration reduction device - Google Patents
Resonant frequency self-tracking giant magnetostrictive vehicle suspension vibration reduction device Download PDFInfo
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- CN104385874A CN104385874A CN201410643718.2A CN201410643718A CN104385874A CN 104385874 A CN104385874 A CN 104385874A CN 201410643718 A CN201410643718 A CN 201410643718A CN 104385874 A CN104385874 A CN 104385874A
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Abstract
The invention discloses a resonant frequency self-tracking giant magnetostrictive vehicle suspension vibration reduction device. The advantages of a giant magnetostrictive material that the energy density is great, the conversion efficiency is high and the responding speed is rapid are utilized, so that the giant magnetostrictive material is embedded into the vehicle suspension vibration reduction device; mechanical energy is converted into electromagnetic energy by a magnetostrictive converse effect and an electromagnetic induction principle; resonant frequency points of a plurality of LRC oscillation circuits are adjusted by a controller with a frequency tracking function, so that the circuit can reach a resonant energy consumption state and multi-mode passive vibration reduction is realized; a vibration reduction control signal is sent out by a control circuit and the vibration is balanced by driving a GMM through the magnetostrictive positive effect to realize active vibration reduction. The resonant frequency self-tracking giant magnetostrictive vehicle suspension vibration reduction device has the beneficial effects that the resonant frequency self-tracking of the vibration reduction device is realized; the structure is simple, the respond is rapid, and the vibration reduction effect is good.
Description
Technical field
The present invention relates to a kind of vehicle suspension vibration damper, the ultra-magnetic telescopic vehicle suspension vibration damper of particularly a kind of resonant frequency autotracking.
Background technology
Vehicle suspension can produce vibration because elastic element is subject to impact, affects safety and the ride comfort of vehicle traveling.In order to avoid Vibration of Vehicle Suspensions brings adverse influence, can at vehicle suspension mounting dampers to reach the object of vibration damping.
Mostly the shock absorber of vehicle suspension is hydraulic shock absorber, its principle of work when between vehicle frame (or vehicle body) and vehicle bridge, is subject to vibration when there is relative motion, piston in shock absorber moves up and down, and the fluid in shock absorber chamber just flows in another chamber from a chamber through different holes repeatedly.Friction now between hole wall and fluid and the intermolecular interior friction of fluid form dumping force to vibration, make automobile vibrational energy be converted into fluid heat energy, then are dispersed in air by shock absorber.
Rigidity and the vibration characteristic of above-mentioned traditional spring mass-damping type vehicle suspension vibration damper are superimposed on vehicle suspension, and the frequency response characteristic of vehicle suspension is additional on shock absorber, and show antiresonance feature at the fixing free-running frequency of shock absorber.The damping of shock absorber can affect attenuation characteristic when oscillation frequency exceedes system antiresonance response, thus changes the vibration characteristic of system, realizes actv. vibration damping.But resonant frequency and the damping coefficient of above-mentioned traditional vehicle suspension vibration damper are fixed, cause shock absorber cannot adapt to complicated Vehicular vibration operating mode.
Many researchists have carried out the research of self-adaptive damping coefficient shock absorber in recent years, and the damping adaptive of these shock absorbers adopts two kinds of methods substantially: first method changes resistance of shock absorber by regulating the hole size between shock absorber chamber; Second method realizes the change of resistance of shock absorber by the viscosity changing shock absorber inner fluid.Based on first method, Chinese invention patent 2010105522620 proposes a kind of circular hole by being drilled with specified quantity, position and size at the clutch release slave cylinder tube wall of traditional double-cylinder hydraulic damper, changes the shock absorber area of passage that fluid flows through under different operating mode and reaches the object changing dumping force.The upper piston body of the shock absorber that Chinese invention patent 2005100212129 proposes and lower piston body are provided with corresponding fluid opening separately in corresponding position, and upper piston body with have one in lower piston body at least and be connected with engine installation, can rotate under the driving of engine installation, fluid opening is misplaced, change the sectional area of fluid circulation passage, change fluid flows to another cavity total amount flow velocity from a cavity, reach the requirement of adjustment damping.Based on second method, US Patent No. 7112474B2 proposes a kind of magnetorheological adaptive damping device, by regulating magnetic field to change magnetic flow liquid viscosity, realizing resistance of shock absorber size and controlling.Chinese invention patent 200710068598.8,201010241273.7,201010249025.7 propose a kind of magneto-rheological combined damping control method and device, and comprehensive use magnetorheological fluid damp control technology and giant magnetostrictive material damping along separate routes, realizes resistance of shock absorber and control.
The self-adaptive damping coefficient shock absorber of above-mentioned Patent design achieves the adjustable control of damping coefficient, but be no matter the mechanical type damping control technology by changing hole size, or magnetorheological fluid damp control technology or giant magnetostrictive material damping along separate routes, its resonant frequency is all fixing.Therefore above-mentioned self-adaptive damping coefficient shock absorber can only have higher energy conversion efficiency in narrower resonance frequency band wide region, the mechanical energy of vibration is effectively dissipated.Under actual condition, the oscillation frequency of vehicle suspension, with the various factors such as road conditions, load, is not often in the resonance frequency band wide region of shock absorber, and the effectiveness in vibration suppression of shock absorber is deteriorated.For improving effective damping frequency range of shock absorber, be necessary the ultra-magnetic telescopic vehicle suspension vibration damper designing autotracking resonant frequency.
Summary of the invention
For above-mentioned prior art Problems existing, the invention provides a kind of ultra-magnetic telescopic vehicle suspension vibration damper of resonant frequency autotracking, autotracking can be carried out to oscillation frequency, make shock absorber effectively can reduce Vibration of Vehicle Suspensions in wider frequency limit, and structure is simple, response rapidly.
To achieve these goals, the technical solution used in the present invention is: a kind of ultra-magnetic telescopic vehicle suspension vibration damper of resonant frequency autotracking, comprises vehicle suspension, signal condition amplifying circuit, frequency-discriminating circuit, vibration damping controller; Described vehicle suspension vibration damper passes to signal condition amplifying circuit by sending GMM transducing signal, and according to this by frequency-discriminating circuit, vibration damping controller; Vibration damping controller realizes initiatively GMM damping and passive GMM damping along separate routes along separate routes by active damping signal generator and resonance energy consuming circuitry.
The present invention also provides a kind of ultra-magnetic telescopic vehicle suspension shock attenuation unit of resonant frequency autotracking, comprises urceolus, is built-in with the soft magnetic bodies inner core of GMM and control circuit system.
The two ends of soft magnetic bodies inner core are connected with piston rod with pilot piston respectively, and are fixed on urceolus by elastic element.
The two ends being up and down arranged on the GMM in soft magnetic bodies inner core are connected with upper permanent magnet with lower permanent magnet respectively, and its periphery is wound with coil.
Control circuit system involving vibrations analysis controling circuit and GMM control circuit.
Vibration analysis control circuit is made up of coil, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping control circuit.
Described GMM control circuit is the passive GMM of single mode damping control circuit, multi-modal shunt damping control circuit or main passive hybridization GMM damping control circuit one along separate routes along separate routes.
Described single mode passive GMM shunt damping control circuit is by coil, resistance R, tunable capacitor C
xform.By tunable capacitor C
x, make coil, resistance R, tunable capacitor C
xthe resonance circuit formed is in resonance point.The electric energy that Suspension System Performance of Vehicle Model energy is changed into by counter magnetostriction effect farthest to dissipate with the form of heat energy, thus can realize the target of vibration damping at resonance point.
Described multi-modal shunt damping control circuit, by multiple LRC tuned circuit, is specially resistance R1, C
x1lRC circuit in parallel, electric capacity C2, R2 that described LRC circuit bag is connected successively and a LC antiresonant circuit
,on the passive GMM of single mode along separate routes damping control circuit basis, multi-modal passive GMM adopts along separate routes and realizes multi-modal shunt damped vibration control every current circuit principle, can effectively suppress multiple vibration frequency components of vibration simultaneously.
Described master passive hybridization GMM along separate routes damping control circuit by coil, resistance R, current source i, tunable capacitor C
xform.ACTIVE CONTROL is then produce the vibration reduction control signal with vibration signal antiphase according to Vibration of Vehicle Suspensions, drives GMM to offset vibration by magnetostriction effect.The main passive hybridization GMM controlled control that damping controls along separate routes can make structure more stable, and ACTIVE CONTROL can realize better control effects.
Described elastic element is spring.
The present invention is based on GMM transduction principle, integrated vibration signal frequency discrimination technology, define a kind of ultra-magnetic telescopic vehicle suspension vibration damping up-to-date technology of resonant frequency autotracking.Passive GMM of the present invention along separate routes damping controls to utilize resonance circuit GMM when resonance point to have the feature of maximum conversion efficiency, is thermal dissipation by Vibration of Vehicle Suspensions Conversion of Energy.The passive GMM of master of the present invention along separate routes damping controls to adopt GMM to achieve active damping, and the effectiveness in vibration suppression main passive GMM shunt damping being controlled with passive vibration damping combined action is more desirable.Above-mentioned vehicle suspension damping technology can carry out autotracking to oscillation frequency, makes shock attenuation unit effectively can reduce Suspension System Performance of Vehicle Model in wider frequency limit, overcomes the shortcoming that conventional truck suspension oscillation damping method operational frequency bandwidth is narrower.And the vehicle suspension damping device structure of the present invention's design is simple, response rapidly, can adapt to the needs of vehicle suspension vibration damping under complex working condition.
Accompanying drawing explanation
Fig. 1 is structured flowchart of the present invention.
Fig. 2 is vibration damping controller workflow diagram.
Fig. 3 is the ultra-magnetic telescopic vehicle suspension damping device structure figure of resonant frequency autotracking.
Fig. 4 is passive GMM damping control schematic diagram along separate routes.
Fig. 5 is the passive GMM shunt impedance-frequency characteristic figure of single mode.
Fig. 6 is multi-modal passive GMM shunt impedance-frequency characteristic figure.
Fig. 7 is main passive hybridization GMM damping control schematic diagram along separate routes.
In figure: 1, urceolus, 2, spring, 3, pilot piston, 4, soft magnetic bodies inner core, 5, lower permanent magnet, 6, coil, 7, GMM, 8, upper permanent magnet, 9, piston rod.
Detailed description of the invention
Below in conjunction with accompanying drawing, the invention will be further described.
Be structured flowchart of the present invention as shown in Figure 1, comprise vehicle suspension, signal condition amplifying circuit, frequency-discriminating circuit, vibration damping controller; Described vehicle suspension shock attenuation unit passes to signal condition amplifying circuit by sending GMM transducing signal, and according to this by frequency-discriminating circuit, vibration damping controller; Vibration damping controller realizes initiatively GMM damping and passive GMM damping along separate routes along separate routes by active damping signal generator and resonance energy consuming circuitry.It is the magnetic domain brought by vibration in GMM deflection is coupled to signal condition amplifying circuit at the voltage signal that coil induces through transforming circuit carry out conditioning amplification that coil, GMM transforming circuit, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping controller constitute its effect of vibration perception circuit, by the frequency component of frequency-discriminating circuit determination Vibration of Vehicle Suspensions, determine suitable vibration reduction strategy according to Vibration Condition on this basis.The vibration of vehicle suspension can produce changes of magnetic field by counter magnetostriction effect in GMM7, causes producing induced voltage in coil 6.Induced voltage signal, by after the process of signal condition amplifying circuit, is determined the oscillation frequency of vehicle suspension by frequency-discriminating circuit.Vibration damping controller regulates active damping signal generator and resonance energy consuming circuitry according to the oscillation frequency of vehicle suspension, realizes main passive GMM damping control along separate routes.
The vibration reduction strategy diagram of circuit of vibration damping controller as shown in Figure 2, the frequency distribution of the oscillation frequency determination vehicle suspension principal vibration energy that vibration damping controller is obtained by frequency-discriminating circuit.If vibrational energy distribution is at a Frequency point, then adopt the passive GMM of single mode damping control along separate routes; If vibrational energy distribution is at multiple Frequency point, then adopt multi-modal passive GMM damping control along separate routes.Determine to adopt passive GMM shunt damping to control or main passive GMM damping control along separate routes according to vehicle suspension size simultaneously.After determining vibration reduction strategy, by change-over switch, circuit is switched to required shock absorption circuit.On this basis, regulate tunable capacitor with parameters such as the oscillation frequency of the resonant frequency and initiatively GMM shunt that adjust passive GMM shunt and amplitudes.
As shown in Figure 3, in the urceolus 1 of the ultra-magnetic telescopic vehicle suspension system shock attenuation unit of resonant frequency autotracking, soft magnetic bodies inner core 4 is installed, the two ends of soft magnetic bodies inner core 4 are connected with piston rod 9 with pilot piston 3 respectively, be fixed in urceolus 1 by spring 2, the two ends being up and down arranged on the GMM7 in soft magnetic bodies inner core 4 are connected with upper permanent magnet 8 with lower permanent magnet 5 respectively, and its periphery is wound with coil 6.GMM7, lower permanent magnet 5, soft magnetic bodies inner core 4 and upper permanent magnet 8 constitute magnetic loop, and coil 6, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping control circuit constitute vibration analysis control circuit.Coil 6, resistance R, tunable capacitor Cx constitute passive GMM damping control circuit along separate routes.Coil 6, resistance R, current source i, tunable capacitor Cx constitutes main passive hybridization GMM damping control circuit along separate routes.The magnetic loop that GMM, permanent magnet and soft magnetic bodies inner core are formed.
Working process of the present invention is as follows:
Passive GMM along separate routes damping control process as shown in Figure 4, during initial condition, GMM7 lower permanent magnet 5, on permanent magnet 8 effect under, its magnetic domain deflects vertically.Prefabricating load F is applied on shock absorber by piston rod 9, and to be provided support counter-force by spring 2.When vehicle suspension system produces vibration, vibrational load is added on prefabricating load F, the magnetic domain of GMM7 inside is deflected, is changed, and then produce induced voltage by the magnetic flow of GMM7 in coil.After induced voltage conditioning being amplified, obtained the oscillation frequency of vehicle suspension system by frequency-discriminating circuit.Vibration damping controller determines the passive GMM of employing single mode damping control or multi-modal passive GMM damping control along separate routes along separate routes according to the dominant frequency component quantity of vibration.With Fig. 4 example, abatement that is single or two vibration frequency components can be realized.When oscillation frequency changes, by the tunable capacitor Cx1 in adjustment RC circuit and Cx2 value, make LRC circuit be in resonance condition all the time, guarantee that the inducing current in coil is converted into thermal energy consumption as far as possible, can effectively suppress the single of vibration or two vibration frequency components simultaneously.
As shown in Figure 5, resonance circuit has maximum impedance at resonant frequency f0 place to the impedance frequency characteristics curve of single mode passive GMM shunt damping, and now RC circuit is in resonance condition, the inducing current in coil at utmost can be converted into thermal energy consumption.
The impedance frequency characteristics curve of multi-modal passive GMM shunt damping as shown in Figure 6, resonance circuit has maximum impedance at resonant frequency f1 and f2 place, now RC circuit is all in resonance condition in frequency f 1 and f2, inducing current in coil at utmost can be converted into thermal energy consumption, be applicable to the vibration that elimination two frequency components are larger.
As shown in Figure 7, its circuit seals in active current source to main passive hybridization GMM shunt damping control process in LRC circuit.Damping control process is similar along separate routes for the Passive Control working process of this circuit and above-mentioned passive GMM, and its ACTIVE CONTROL process is then the vibration signal generation vibration reduction control signal according to sensing, is applied to coil 6 rear drive GMM7 to realize the ACTIVE CONTROL vibrated.The main passive hybridization GMM controlled control that damping controls along separate routes can make structure more stable, and ACTIVE CONTROL can realize better control effects.
The GMM mentioned herein is giant magnetostrictive material; as Terfeol-D; above-mentioned detailed description of the invention is used for explaining and the present invention is described; instead of limit the invention; in the protection domain of spirit of the present invention and claim; the any amendment make the present invention and change, all fall into protection scope of the present invention.
Claims (6)
1. a ultra-magnetic telescopic vehicle suspension shock attenuation unit for resonant frequency autotracking, is characterized in that comprising vehicle suspension, GMM transforming circuit, signal condition amplifying circuit, frequency-discriminating circuit, vibration damping controller; Described vehicle suspension resonant frequency autotracking passes to signal condition amplifying circuit by sending GMM transducing signal, and according to this by frequency-discriminating circuit, vibration damping controller; Vibration damping controller realizes initiatively GMM damping and passive GMM damping along separate routes along separate routes by active damping signal generator and resonance energy consuming circuitry.
2. a ultra-magnetic telescopic vehicle suspension damping device structure for resonant frequency autotracking, the soft magnetic bodies inner core of the GMM that it is characterized in that, comprise urceolus, is built-in with and control circuit system;
The two ends of soft magnetic bodies inner core are connected with piston rod with pilot piston respectively, and are fixed on urceolus by elastic element;
The two ends being up and down arranged on the GMM in soft magnetic bodies inner core are connected with upper permanent magnet with lower permanent magnet respectively, and its periphery is wound with coil;
Control circuit system involving vibrations analysis controling circuit and GMM control circuit;
Vibration analysis control circuit is made up of coil, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping control circuit;
Described GMM control circuit is the passive GMM of single mode damping control circuit, multi-modal shunt damping control circuit or main passive hybridization GMM damping control circuit one along separate routes along separate routes;
The ultra-magnetic telescopic vehicle suspension shock attenuation unit of a kind of resonant frequency autotracking according to claim 2, is characterized in that described single mode passive GMM shunt damping control circuit is by coil, resistance R, tunable capacitor C
xform.
3. the ultra-magnetic telescopic suspension device for vehicle of a kind of resonant frequency autotracking according to claim 2, is characterized in that, described multi-modal shunt damping control circuit is made up of multiple LRC tuned circuit.
4. the ultra-magnetic telescopic suspension device for vehicle of a kind of resonant frequency autotracking according to claim 2, is characterized in that, described master passive hybridization GMM along separate routes damping control circuit by coil, resistance R, current source i, tunable capacitor C
xform.
5. the ultra-magnetic telescopic suspension device for vehicle of a kind of resonant frequency autotracking according to claim 2, is characterized in that, described elastic element is spring.
6. the ultra-magnetic telescopic suspension device for vehicle of a kind of resonant frequency autotracking according to claim 2, it is characterized in that, described multi-modal shunt damping control circuit comprises the LRC circuit in parallel with resistance R1, Cx1, electric capacity C2, R2 that described LRC circuit bag is connected successively and a LC antiresonant circuit.
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Cited By (4)
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| CN105508495A (en) * | 2015-12-15 | 2016-04-20 | 西安科技大学 | Energy feeding magnetorheological elastomer vehicle vibration reducing device and control method thereof |
| CN107807532A (en) * | 2017-11-30 | 2018-03-16 | 北京航空航天大学 | A kind of adaptive inversion vibration isolation control method for ultra-magnetic telescopic vibration-isolating platform |
| CN111425552A (en) * | 2020-04-29 | 2020-07-17 | 珠海格力电器股份有限公司 | Vibration damper and refrigeration equipment |
| CN114448161A (en) * | 2022-01-27 | 2022-05-06 | 中国长江三峡集团有限公司 | High-temperature superconducting magnetic suspension flywheel with axial vibration isolation function |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114448161B (en) * | 2022-01-27 | 2023-10-13 | 中国长江三峡集团有限公司 | High-temperature superconductive magnetic suspension flywheel with axial vibration isolation function |
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Denomination of invention: A damping device of giant magnetostrictive vehicle suspension with resonance frequency self tracking Effective date of registration: 20200805 Granted publication date: 20160629 Pledgee: Bank of China Limited by Share Ltd. Xuzhou Copper Mt branch Pledgor: XUZHOU HUAXIA ELECTRONICS Co.,Ltd. Registration number: Y2020320000180 |